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EP1430242A1 - High-pressure sealing assembly - Google Patents

High-pressure sealing assembly

Info

Publication number
EP1430242A1
EP1430242A1 EP02769938A EP02769938A EP1430242A1 EP 1430242 A1 EP1430242 A1 EP 1430242A1 EP 02769938 A EP02769938 A EP 02769938A EP 02769938 A EP02769938 A EP 02769938A EP 1430242 A1 EP1430242 A1 EP 1430242A1
Authority
EP
European Patent Office
Prior art keywords
sealing ring
pressure
peripheral surface
sealing
outer peripheral
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP02769938A
Other languages
German (de)
French (fr)
Other versions
EP1430242B1 (en
Inventor
Holger Jordan
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Busak and Shamban Deutschland GmbH
Original Assignee
Busak and Shamban GmbH and Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Busak and Shamban GmbH and Co filed Critical Busak and Shamban GmbH and Co
Publication of EP1430242A1 publication Critical patent/EP1430242A1/en
Application granted granted Critical
Publication of EP1430242B1 publication Critical patent/EP1430242B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3208—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip provided with tension elements, e.g. elastic rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/164—Sealings between relatively-moving surfaces the sealing action depending on movements; pressure difference, temperature or presence of leaking fluid

Definitions

  • the invention relates to a high-pressure sealing arrangement for sealing a gap between two mutually concentric, mutually movable machine parts, of which a first machine part has a groove and a second machine part has an outer peripheral surface opposite the groove.
  • Such a high-pressure seal arrangement has become known, for example, from DE-OS 43 23 266 A1.
  • the known arrangement for sealing a gap between two mutually concentric, mutually movable machine parts has a sealing ring in the groove, which is fixed in the machine element.
  • the sealing ring is flexible in relation to the forces acting radially and axially on the sealing ring.
  • the pressure-dependent deformations of the sealing ring are reversible, i.e. if the fluid pressure on the high-pressure side drops, the sealing ring automatically reforms into its original profile.
  • the sealing surface or sealing edge can be relieved of pressure.
  • the invention is based on the object of developing the known sealing arrangement in such a way that the frictional force and extrusion behavior in the area of the dynamic seal is further improved.
  • a high-pressure seal arrangement in which a sealing ring made of an extrusion-resistant material and a clamping ring made of an elastomeric material are provided in the groove, with a low-pressure-side profile area of the sealing ring being subjected to fluid pressure
  • Outer peripheral surface can be deflected, the pressure-dependent deflection of the sealing ring automatically regressing in the direction of the starting position of the sealing ring in the depressurized state when the pressure is reduced, the sealing ring - seen in cross section and in the depressurized state - having a profiled sealing ring surface facing the outer circumferential surface, which at least with respect to the low-pressure side profile area merges into a heel area spaced from the outer circumferential surface with a first distance d, which in turn merges into a heel area with a second distance d 2 that is more distant from the outer circumferential surface.
  • the profiling of the sealing ring surface can be designed in the manner of teeth, waves or steps.
  • the sealing ring surface has a support foot or a support section with the prestressed sealing surface. This creates a seal at low fluid pressures. With higher pressurization, the support foot or support section tilts and the sealing surface is relieved of pressure, an edge, step or projection with an angular or rounded design on the low-pressure side heel surface touches down and becomes a sealing edge or sealing surface. There is thus an improved pressure relief of the sealing ring elements abutting the outer peripheral surface of the second machine part.
  • the sealing ring is made of a material that is harder than the clamping ring with a larger modulus of elasticity. The essence of the invention is seen in the choice of materials and the multi-stage sealing ring surface in the area of the outer peripheral surface of the second machine part. This multi-stage sealing ring surface can be placed on the outer peripheral surface after pivoting the sealing ring. This reduces friction when the second machine part rotates and translates.
  • the sealing ring is preferably symmetrical.
  • the pressure-dependent deflection of the sealing ring automatically regresses in the direction of the initial position of the sealing ring in the depressurized state when the pressure is lowered, the sealing ring - seen in cross section and in the depressurized state - having a profiled sealing ring surface facing the outer peripheral surface, which is stepped on both sides in two from the outer peripheral surface spaced sales areas passes, which in turn merge over at least one edge in side surfaces.
  • the heel surfaces merge into the side surfaces via inclined surfaces running transversely to the outer peripheral surface.
  • a wedge gap is formed on the high pressure side and the low pressure side.
  • the inclined surface on the high-pressure side can be undercut by the fluid when pressure is applied and support pivoting of the sealing ring.
  • the high pressure seal arrangement according to the invention can for
  • Rotary unions can be used in hydraulics.
  • Fig. 1 shows a sealing arrangement in cross section without or with little
  • Fig. 2 shows the sealing arrangement of Figure 1 when high pressure is applied.
  • Fig. 1 shows a sealing ring 1 made of an extrusion-resistant rigid material, such as polyurethane or similar materials, and a clamping ring 2 made of an elastomeric material.
  • the sealing ring 1 and the clamping ring 2 are installed in a groove 3 of a first machine part 4, which is arranged opposite a rotatable second machine part 5.
  • the sealing ring 1 and the clamping ring 2 together have an oversize compared to the groove 3. If the sealing ring 1 and the clamping ring 2 are introduced into the groove 3, a sealing surface 6 of a support foot or support section is pressed onto an outer peripheral surface 7 of the second machine part 5 so that the interference in the static sealing area can be reduced.
  • the clamping ring 2 is prestressed on the groove base 8 and is in contact with the groove base 8 and a groove flank 1 1 on the low-pressure side via contact lines 9 and 10.
  • the contact lines 9 and 10 have the function of statically acting sealing edges.
  • the high pressure side is marked with H and the low pressure side with N.
  • the sealing ring is pressurized with fluid.
  • the sealing ring 1 has an essentially trapezoidal cross-sectional shape, the sealing ring side facing the outer peripheral surface 7 being designed with multiple profiles.
  • a central sealing surface 6 assigned to a dynamic sealing region is stepped on both sides in two from the outer peripheral surface 7 spaced-apart heel areas 13 and 14 so that free spaces 1 5 and 1 6 form.
  • the heel surfaces 1 3 and 14 are each connected to side surfaces 1 9 and 20 of the sealing ring 1 via inclined surfaces 1 7 and 1 8 running transversely to the outer peripheral surface 7.
  • the inclined surfaces 1 7 and 1 8 intersect with the side surfaces 1 9 and 20 in edges 21 and 22.
  • the heel surfaces 1 3 and 1 4 intersect with the inclined surfaces 1 7 and 1 8 in edges 23 and 24.
  • the rear side 25 of the sealing ring 1 rests on the clamping ring 2.
  • the sealing ring 1 seals a gap 26 between the machine parts 4 and 5.
  • Relevant according to the invention are two different distances d ⁇ and d 2 , which is not constant in the present case due to the inclined surface. For example, if training as a level, d 2 would also be constant.
  • the 2 shows the sealing ring 1 under pressure loading from the high pressure side H.
  • the sealing ring 1 is loaded with a pressure P in the direction of arrow 27.
  • the sealing ring 1 is pressed against the groove flank 11 by the fluid pressure P. Due to the profile of the sealing ring 1, the sealing ring 1 is pivoted toward the low-pressure side N, so that the edge 23 is pressed against the outer peripheral surface 7.
  • a closed annular space 28 is formed by the edge 23, the shoulder surface 13 and the central sealing surface 6.
  • the edge 23 and the partially pressure-relieved sealing surface 6 assume the function of a dynamic seal.
  • the sealing ring 1 lies flat over the sealing surface 6 and linearly over the edge 23 on the outer peripheral surface 7.
  • Both the sealing ring 1 and the clamping ring 2 are pressed on the low-pressure side flank 1 1 and lie flat.
  • the inclined surface 1 8 is raised by the fluid pressure P.
  • the back 25 is curved to the clamping ring 2.
  • the spacing of the sales surface 1 4 to the outer peripheral surface 7 increases. The fluid can penetrate under the shoulder surface 14.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Devices (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Abstract

The invention relates to a high-pressure sealing assembly for sealing a gap (26) between two concentric machine parts (4, 5) that can be displaced in relation to one another, the first of said machine parts (4) having a groove (3) and the second of said machine parts (5) having an external peripheral surface (7), which lies opposite the groove (3). A sealing ring (1) consisting of extrusion-resistant material and a retaining ring (2) consisting of an elastomeric substance are provided in the groove (3). A contoured region of the sealing ring (1) on the low-pressure side can be deflected in relation to the external peripheral surface (7), under the impingement of a fluidic pressure. The pressure-dependent deflection of the sealing ring (1) automatically recedes with a drop in pressure in the direction of the initial position of the sealing ring (1) in the pressureless state. The sealing ring (1) has, (viewed in cross-section and in the pressureless state) a contoured sealing ring surface (6) facing the external peripheral surface (7). Said sealing ring surface, at least with respect to the contoured region on the low-pressure side, runs into a relief surface (13), which lies at a first distance d1 from the external peripheral surface (7), said relief surface in turn running into a lateral surface (20) that lies at a greater second distance d2 from the external peripheral surface (7).

Description

Bezeichnung der Erfindung:Title of the invention:
HochdruckdichtungsanordnungHigh pressure seal assembly
BESCHREIBUNGDESCRIPTION
Die Erfindung betrifft eine Hochdruckdichtungsanordnung zum Abdichten eines Spalts zwischen zwei zueinander konzentrischen, gegeneinander beweglichen Maschinenteilen, von denen ein erstes Maschinenteil eine Nut und zweites Maschinenteil eine der Nut gegenüberliegende Außenumfangsfläche aufweist. Stand der TechnikThe invention relates to a high-pressure sealing arrangement for sealing a gap between two mutually concentric, mutually movable machine parts, of which a first machine part has a groove and a second machine part has an outer peripheral surface opposite the groove. State of the art
Eine derartige Hochdruckdichtungsanordnung ist beispielsweise durch die DE-OS 43 23 266 A 1 bekannt geworden.Such a high-pressure seal arrangement has become known, for example, from DE-OS 43 23 266 A1.
Die bekannte Anordnung zum Abdichten eines Spalts zwischen zwei zueinander konzentrischen, gegeneinander beweglichen Maschinenteilen weist in der Nut einen Dichtring auf, der ortsfest im Maschinenelement montiert ist. Der Dichtring ist gegenüber radial und axial auf den Dichtring wirkenden Kräften flexibel. Die druckabhängigen Verformungen des Dichtrings sind reversibel, d.h., bei fallendem Fluiddruck an der Hochdruckseite bildet sich der Dichtring selbständig in seine Ausgangsprofilierung zurück. Die Dichtfläche bzw. Dichtkante kann druckentlastet werden.The known arrangement for sealing a gap between two mutually concentric, mutually movable machine parts has a sealing ring in the groove, which is fixed in the machine element. The sealing ring is flexible in relation to the forces acting radially and axially on the sealing ring. The pressure-dependent deformations of the sealing ring are reversible, i.e. if the fluid pressure on the high-pressure side drops, the sealing ring automatically reforms into its original profile. The sealing surface or sealing edge can be relieved of pressure.
Aufgabe der ErfindungObject of the invention
Der Erfindung liegt die Aufgabe zugrunde, die bekannte Dichtungsanordnung derart weiterzubilden, daß das Reibkraft- und Extrusionsverhalten im Bereich der dynamischen Abdichtung weiter verbessert wird.The invention is based on the object of developing the known sealing arrangement in such a way that the frictional force and extrusion behavior in the area of the dynamic seal is further improved.
Gegenstand und Vorteile der ErfindungObject and advantages of the invention
Diese Aufgabe wird durch eine Hochdruckdichtungsanordnung gelöst, bei der in der Nut ein Dichtring aus einem extrusionsfesten Material und ein Spannring aus einem elastomeren Werkstoff vorgesehen sind, wobei ein niederdruckseitiger Profilbereich des Dichtrings unter Fluiddruckbeaufschlagung zurThis object is achieved by a high-pressure seal arrangement in which a sealing ring made of an extrusion-resistant material and a clamping ring made of an elastomeric material are provided in the groove, with a low-pressure-side profile area of the sealing ring being subjected to fluid pressure
Außenumfangsfläche auslenkbar ist, wobei sich die druckabhängige Auslenkung des Dichtrings bei einer Druckerniedrigung selbsttätig in Richtung der Ausgangslage des Dichtrings im drucklosen Zustand zurückbildet, wobei der Dichtring - im Querschnitt und im drucklosen Zustand gesehen - eine profilierte der Außenumfangsfläche zugewandte Dichtringfläche aufweist, welche zumindest bezüglich des niederdruckseitigen Profilbereichs in eine von der Außenumfangsfläche beabstandete Absatzfläche mit einem ersten Abstand d, übergeht, welche wiederum in eine von der Außenumfangsfläche stärker beabstandete Absatzfläche Seitenfläche mit einem zweiten Abstand d2 übergeht. Die Profilierung der Dichtringfläche kann zackenartig, wellenartig oder treppenartig ausgestaltet sein. Die Dichtringfläche weist einen Stützfuß oder einen Stützabschnitt mit der vorgespannten Dichtfläche auf. Dies bewirkt eine Abdichtung bei niederen Fiuiddrücken. Bei höherer Druckbeaufschlagung verkippt der Stützfuß oder Stützabschnitt und die Dichtfläche wird druckentlastet, eine Kante, Stufe oder Vorsprung mit einer kantigen oder runden Ausbildung an der niederdruckseitigen Absatzfläche setzt auf und wird zu einer Dichtkante oder Dichtfläche. Es findet somit eine verbesserte Druckentlastung der an der Außenumfangsfläche des zweiten Maschinenteils anliegenden Dichtringelemente statt. Der Dichtring ist aus einem gegenüber dem Spannring härteren Material mit einem größeren E-Modul hergestellt. Der Kern der Erfindung wird in der Wahl der Werkstoffe und der mehrstufigen Dichtringfläche im Bereich der Außenumfangsfläche des zweiten Maschinenteils gesehen. Diese mehrstufige Dichtringfläche kann nach Verschwenken des Dichtrings auf der Außenumfangsfläche aufsetzen. Die Reibung verringert sich dadurch bei Rotation und Translation des zweiten Maschinenteils.Outer peripheral surface can be deflected, the pressure-dependent deflection of the sealing ring automatically regressing in the direction of the starting position of the sealing ring in the depressurized state when the pressure is reduced, the sealing ring - seen in cross section and in the depressurized state - having a profiled sealing ring surface facing the outer circumferential surface, which at least with respect to the low-pressure side profile area merges into a heel area spaced from the outer circumferential surface with a first distance d, which in turn merges into a heel area with a second distance d 2 that is more distant from the outer circumferential surface. The profiling of the sealing ring surface can be designed in the manner of teeth, waves or steps. The sealing ring surface has a support foot or a support section with the prestressed sealing surface. This creates a seal at low fluid pressures. With higher pressurization, the support foot or support section tilts and the sealing surface is relieved of pressure, an edge, step or projection with an angular or rounded design on the low-pressure side heel surface touches down and becomes a sealing edge or sealing surface. There is thus an improved pressure relief of the sealing ring elements abutting the outer peripheral surface of the second machine part. The sealing ring is made of a material that is harder than the clamping ring with a larger modulus of elasticity. The essence of the invention is seen in the choice of materials and the multi-stage sealing ring surface in the area of the outer peripheral surface of the second machine part. This multi-stage sealing ring surface can be placed on the outer peripheral surface after pivoting the sealing ring. This reduces friction when the second machine part rotates and translates.
Bevorzugt ist der Dichtring symmetrisch ausgebildet. Die druckabhängige Auslenkung des Dichtrings bildet sich bei einer Druckerniedrigung selbsttätig in Richtung der Ausgangslage des Dichtrings im drucklosen Zustand zurück, wobei der Dichtring - im Querschnitt und im drucklosen Zustand gesehen - eine profilierte der Außenumfangsfläche zugewandte Dichtringfläche aufweist, welche beidseitig stufenförmig in zwei von der Außenumfangsfläche beabstandete Absatzflächen übergeht, die wiederum über mindestens eine Kante in Seitenflächen übergehen.The sealing ring is preferably symmetrical. The pressure-dependent deflection of the sealing ring automatically regresses in the direction of the initial position of the sealing ring in the depressurized state when the pressure is lowered, the sealing ring - seen in cross section and in the depressurized state - having a profiled sealing ring surface facing the outer peripheral surface, which is stepped on both sides in two from the outer peripheral surface spaced sales areas passes, which in turn merge over at least one edge in side surfaces.
Bei einer Weiterbildung der Erfindung gehen die Absatzflächen über quer zur Außenumfangsfläche verlaufende Schrägflächen in die Seitenflächen über. Es bildet sich jeweils zur Hochdruckseite und zur Niederdruckseite ein Keilspalt aus. Die hochdruckseitige Schrägfläche kann bei Druckbeaufschlagung vom Fluid Untergriffen werden und ein Verschwenken des Dichtrings unterstützen.In a further development of the invention, the heel surfaces merge into the side surfaces via inclined surfaces running transversely to the outer peripheral surface. A wedge gap is formed on the high pressure side and the low pressure side. The inclined surface on the high-pressure side can be undercut by the fluid when pressure is applied and support pivoting of the sealing ring.
Die erfindungsgemäße Hochdruckdichtungsanordnung kann fürThe high pressure seal arrangement according to the invention can for
Drehdurchführungen in der Hydraulik verwendet werden. ZeichnungRotary unions can be used in hydraulics. drawing
Ein Ausführungsbeispiel der erfindungsgemäßen Dichtungsanordnung ist in der schematischen Zeichnung dargestellt und wird in der nachfolgenden Beschreibung erläutert. Die Gegenstände der einzelnen Figuren und Abschnitte der Dichtungsanordnung sind teilweise stark vergrößert und überzogen stark verformt dargestellt, damit die Funktionsweise der Dichtungsanordnung besser ersichtlich ist. Es zeigt:An embodiment of the sealing arrangement according to the invention is shown in the schematic drawing and is explained in the following description. The objects of the individual figures and sections of the sealing arrangement are shown partially greatly enlarged and greatly deformed so that the functioning of the sealing arrangement can be seen more clearly. It shows:
Fig. 1 eine Dichtungsanordnung im Querschnitt ohne oder bei geringerFig. 1 shows a sealing arrangement in cross section without or with little
Druckbeaufschlagung;pressurization;
Fig. 2 die Dichtungsanordnung nach Fig.1 bei Hochdruckbeaufschlagung.Fig. 2 shows the sealing arrangement of Figure 1 when high pressure is applied.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Fig. 1 zeigt einen Dichtring 1 aus einem extrusionsfesten steifen Material, wie Polyurethan oder ähnlichen Materialien, und einen Spannring 2 aus einem elastomeren Werkstoff. Der Dichtring 1 und der Spannring 2 sind in einer Nut 3 eines ersten Maschinenteils 4 eingebaut, das einem rotierbaren zweiten Maschinenteil 5 gegenüberliegend angeordnet ist. Der Dichtring 1 und der Spannring 2 weisen zusammen gegenüber der Nut 3 ein Übermaß auf. Werden der Dichtring 1 und der Spannring 2 in die Nut 3 eingebracht, so wird eine Dichtfläche 6 eines Stützfußes oder Stützabschnitts an eine Außenumfangsfläche 7 des zweiten Maschinenteils 5 angedrückt, damit die Interferenz im statischen Abdichtungsbereich abgebaut werden kann. In der in Fig. 1 gezeigten Einbaulage ist der Spannring 2 am Nutgrund 8 vorgespannt und liegt über Berührungslinien 9 und 1 0 am Nutgrund 8 und einer niederdruckseitigen Nutflanke 1 1 an. Die Berührungslinien 9 und 1 0 haben die Funktion statisch wirkender Dichtkanten.Fig. 1 shows a sealing ring 1 made of an extrusion-resistant rigid material, such as polyurethane or similar materials, and a clamping ring 2 made of an elastomeric material. The sealing ring 1 and the clamping ring 2 are installed in a groove 3 of a first machine part 4, which is arranged opposite a rotatable second machine part 5. The sealing ring 1 and the clamping ring 2 together have an oversize compared to the groove 3. If the sealing ring 1 and the clamping ring 2 are introduced into the groove 3, a sealing surface 6 of a support foot or support section is pressed onto an outer peripheral surface 7 of the second machine part 5 so that the interference in the static sealing area can be reduced. In the installation position shown in FIG. 1, the clamping ring 2 is prestressed on the groove base 8 and is in contact with the groove base 8 and a groove flank 1 1 on the low-pressure side via contact lines 9 and 10. The contact lines 9 and 10 have the function of statically acting sealing edges.
In der Fig. 1 ist mit H die Hochdruckseite gekennzeichnet und mit N die Niederdruckseite. In der Fig. 1 ist der Dichtring fluidniederdruckbeaufschlagt. Der Dichtring 1 weist eine im wesentlichen trapezförmige Querschnittsform auf, wobei die der Außenumfangsfläche 7 zugewandte Dichtringseite mehrfach profiliert ausgebildet ist. Eine zentrale, einem dynamischen Dichtungsbereich zugeordnete Dichtfläche 6 geht beidseitig abgestuft in zwei von der Außenumfangsfläche 7 beabstandete Absatzflächen 13 und 14 über, so dass sich Freiräume 1 5 und 1 6 ausbilden. Die Absatzflächen 1 3 und 14 sind jeweils über quer zur Außenumfangsfläche 7 verlaufende Schrägflächen 1 7 und 1 8 mit Seitenflächen 1 9 und 20 des Dichtrings 1 verbunden. Die Schrägflächen 1 7 und 1 8 schneiden sich mit den Seitenflächen 1 9 und 20 in Kanten 21 und 22. Die Absatzflächen 1 3 und 1 4 schneiden sich mit den Schrägflächen 1 7 und 1 8 in Kanten 23 und 24. Die Rückseite 25 des Dichtrings 1 liegt an dem Spannring 2 an. Der Dichtring 1 dichtet einen Spalt 26 zwischen den Maschinenteilen 4 und 5 ab. Erfindungsgemäß relevant sind zwei unterschiedliche Abstände d^ und d2 , der im vorliegenden Fall durch die Schrägfläche nicht konstant ist. Beispielsweise bei einer Ausbildung als Stufe wäre auch d2 konstant.In Fig. 1, the high pressure side is marked with H and the low pressure side with N. In Fig. 1 the sealing ring is pressurized with fluid. The sealing ring 1 has an essentially trapezoidal cross-sectional shape, the sealing ring side facing the outer peripheral surface 7 being designed with multiple profiles. A central sealing surface 6 assigned to a dynamic sealing region is stepped on both sides in two from the outer peripheral surface 7 spaced-apart heel areas 13 and 14 so that free spaces 1 5 and 1 6 form. The heel surfaces 1 3 and 14 are each connected to side surfaces 1 9 and 20 of the sealing ring 1 via inclined surfaces 1 7 and 1 8 running transversely to the outer peripheral surface 7. The inclined surfaces 1 7 and 1 8 intersect with the side surfaces 1 9 and 20 in edges 21 and 22. The heel surfaces 1 3 and 1 4 intersect with the inclined surfaces 1 7 and 1 8 in edges 23 and 24. The rear side 25 of the sealing ring 1 rests on the clamping ring 2. The sealing ring 1 seals a gap 26 between the machine parts 4 and 5. Relevant according to the invention are two different distances d ^ and d 2 , which is not constant in the present case due to the inclined surface. For example, if training as a level, d 2 would also be constant.
Fig. 2 zeigt den Dichtring 1 unter Druckbelastung von der Hochdruckseite H. Der Dichtring 1 wird in Pfeilrichtung 27 mit einem Druck P belastet. Über den Fluiddruck P wird der Dichtring 1 an die Nutflanke 1 1 gedrückt. Auf Grund der Profilgebung des Dichtrings 1 wird der Dichtring 1 zur Niederdruckseite N hin verschwenkt, so dass die Kante 23 an die Außenumfangsfläche 7 gedrückt ist. Es bildet sich ein geschlossener Ringraum 28 durch die Kante 23, die Absatzfläche 1 3 und die zentrale Dichtfläche 6. Die Kante 23 und die teilweise druckentlastete Dichtfläche 6 übernehmen die Funktion einer dynamischen Abdichtung. Der Dichtring 1 liegt flächenhaft über die Dichtfläche 6 und linienhaft über die Kante 23 an der Außenumfangsfläche 7 an. An der niederdruckseitigen Nutflanke 1 1 werden sowohl der Dichtring 1 als auch der Spannring 2 verpresst und liegen flächenhaft an. Die Schrägfläche 1 8 wird durch den Fluiddruck P angehoben. Die Rückseite 25 wird zum Spannring 2 gekrümmt. Die Beabstandung der Absatzfläche 1 4 zur Außenumfangsfläche 7 nimmt zu. Das Fluid kann unter die Absatzfläche 14 vordringen.2 shows the sealing ring 1 under pressure loading from the high pressure side H. The sealing ring 1 is loaded with a pressure P in the direction of arrow 27. The sealing ring 1 is pressed against the groove flank 11 by the fluid pressure P. Due to the profile of the sealing ring 1, the sealing ring 1 is pivoted toward the low-pressure side N, so that the edge 23 is pressed against the outer peripheral surface 7. A closed annular space 28 is formed by the edge 23, the shoulder surface 13 and the central sealing surface 6. The edge 23 and the partially pressure-relieved sealing surface 6 assume the function of a dynamic seal. The sealing ring 1 lies flat over the sealing surface 6 and linearly over the edge 23 on the outer peripheral surface 7. Both the sealing ring 1 and the clamping ring 2 are pressed on the low-pressure side flank 1 1 and lie flat. The inclined surface 1 8 is raised by the fluid pressure P. The back 25 is curved to the clamping ring 2. The spacing of the sales surface 1 4 to the outer peripheral surface 7 increases. The fluid can penetrate under the shoulder surface 14.
Je nach Größe der Druckbeaufschlagung (Fluiddruck P) ergeben sich eine unterschiedlich starke Verformung an der Nutflanke 1 1 und eine Anpressung oder Beabstandung an die Außenumfangsfläche 7.Depending on the size of the pressurization (fluid pressure P), there is a different degree of deformation on the groove flank 11 and a pressure or spacing on the outer peripheral surface 7.
Diese Verformung ist reversibel und bildet sich bei fallendem Druck zurück. BEZUGSZEICHENLISTEThis deformation is reversible and disappears when the pressure drops. LIST OF REFERENCE NUMBERS
Dichtringseal
Spannringclamping ring
Nutgroove
Maschinenteilmachinery
Maschinenteilmachinery
Dichtflächesealing surface
AußenumfangsflächeOuter circumferential surface
Nutgrundgroove base
Berührungsliniecontact line
Berührungsliniecontact line
Nutflankeflank
Absatzflächeshoulder surface
Absatzflächeshoulder surface
Freiraumfree space
Freiraumfree space
Schrägflächesloping surface
Schrägflächesloping surface
Seitenflächeside surface
Seitenflächeside surface
Schnittlinieintersection
Schnittlinieintersection
Kanteedge
Kanteedge
Rückseiteback
Spaltgap
Pfeilrichtungarrow
Ringraumannulus
Abstand zur AußenumfangsflächeDistance to the outer peripheral surface
Abstand zur Außenumfangsfläche Distance to the outer peripheral surface

Claims

PA T E N T A N S P R ÜC H E PATENT REQUESTS
1 . Hochdruckdichtungsanordnung zum Abdichten eines Spalts (26) zwischen zwei zueinander konzentrischen, gegeneinander beweglichen Maschinenteilen (4, 5), von denen ein erstes Maschinenteil (4) eine Nut (3) und zweites Maschinenteil (5) eine der Nut (3) gegenüberliegende Außenumfangsfläche (7) aufweist, wobei in der Nut (3) ein Dichtring ( 1 ) aus einem extrusionsfesten Material und ein Spannring (2) aus einem elastomeren Werkstoff vorgesehen sind, wobei ein niederdruckseitiger Profilbereich des Dichtrings (1 ) unter Fluiddruckbeaufschlagung zur Außenumfangsfläche (7) auslenkbar ist, wobei sich die druckabhängige Auslenkung des Dichtrings ( 1 ) bei einer Druckerniedrigung selbsttätig in Richtung der Ausgangslage des Dichtrings ( 1 ) im drucklosen Zustand zurückbildet, wobei der Dichtring (1 ) - im Querschnitt und im drucklosen Zustand gesehen - eine profilierte der Außenumfangsfläche (7) zugewandte Dichtringfläche (6) aufweist, welche zumindest bezüglich des niederdruckseitigen Profilbereichs in eine von der Außenumfangsfläche (7) beabstandete Absatzfläche (1 3) mit einem ersten Abstand d, übergeht, welche wiederum in eine von der Außenumfangsfläche (7) stärker beabstandete Absatzfläche (1 3) Seitenfläche (20) mit einem zweiten Abstand d2 übergeht.1 . High-pressure sealing arrangement for sealing a gap (26) between two mutually concentric, mutually movable machine parts (4, 5), of which a first machine part (4) has a groove (3) and second machine part (5) an outer peripheral surface opposite the groove (3) 7), wherein a sealing ring (1) made of an extrusion-resistant material and a tension ring (2) made of an elastomeric material are provided in the groove (3), a low-pressure-side profile area of the sealing ring (1) being deflectable to the outer peripheral surface (7) under fluid pressure the pressure-dependent deflection of the sealing ring (1) automatically regresses in the direction of the initial position of the sealing ring (1) in the depressurized state when the pressure is reduced, the sealing ring (1) - seen in cross section and in the depressurized state - a profiled of the outer peripheral surface ( 7) facing sealing ring surface (6), which at least with respect to the low pressure side Profile area merges into a heel surface (1 3) spaced from the outer circumferential surface (7) at a first distance d, which in turn merges into a heel surface (1 3) at a greater distance from the outer circumferential surface (7) with a second spacing d 2 transforms.
2. Hochdruckdichtungsanordnung nach Anspruch 1 , dadurch gekennzeichnet, dass der Dichtring ( 1 ) unter Fluiddruckbeaufschlagung zur niederdruckseitigen Nutflanke (1 1 ) auslenkbar ist, wobei sich die druckabhängige Auslenkung des Dichtrings (1 ) bei einer Druckerniedrigung selbsttätig in Richtung der Ausgangslage des Dichtrings (1 ) im drucklosen Zustand zurückbildet, wobei der Dichtring (1 ) - im Querschnitt und im drucklosen Zustand gesehen - eine profilierte der Außenumfangsfläche (7) zugewandte Dichtringfläche (6) aufweist, welche beidseitig stufenförmig in zwei von der Außenumfangsfläche (7) beabstandete Absatzflächen (1 3, 1 4) übergeht, die wiederum über mindestens eine Kante (23, 24) in Seitenflächen (1 9, 20) übergehen.2. High-pressure seal arrangement according to claim 1, characterized in that the sealing ring (1) under fluid pressure to the low-pressure side flank (1 1) can be deflected, the pressure-dependent deflection of the sealing ring (1) automatically in the direction of the starting position of the sealing ring (1 ) in the depressurized state, the sealing ring (1) - seen in cross section and in the depressurized state - having a profiled sealing ring surface (6) facing the outer peripheral surface (6), which is stepped on both sides in two heel surfaces (1) spaced apart from the outer peripheral surface (7) 3, 1 4), which in turn merge over at least one edge (23, 24) into side surfaces (1 9, 20).
3. Hochdruckdichtungsanordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Absatzflächen (1 3, 14) über quer zur Außenumfangsfläche verlaufende Schrägflächen (17, 18) in die Seitenflächen {19, 20) übergehen.3. High-pressure seal arrangement according to claim 1 or 2, characterized in that the heel surfaces (1 3, 14) across to The oblique surfaces (17, 18) running on the outer peripheral surface merge into the side surfaces {19, 20).
4. Verwendung der Hochdruckdichtungsanordnung nach Anspruch 1 oder 2 für Drehdurchführungen in der Hydraulik. 4. Use of the high-pressure seal arrangement according to claim 1 or 2 for rotary unions in the hydraulic system.
EP02769938A 2001-09-18 2002-09-13 High-pressure sealing assembly Expired - Lifetime EP1430242B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10145914 2001-09-18
DE10145914A DE10145914A1 (en) 2001-09-18 2001-09-18 High pressure seal assembly
PCT/DE2002/003400 WO2003027545A1 (en) 2001-09-18 2002-09-13 High-pressure sealing assembly

Publications (2)

Publication Number Publication Date
EP1430242A1 true EP1430242A1 (en) 2004-06-23
EP1430242B1 EP1430242B1 (en) 2005-05-25

Family

ID=7699396

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02769938A Expired - Lifetime EP1430242B1 (en) 2001-09-18 2002-09-13 High-pressure sealing assembly

Country Status (9)

Country Link
US (1) US7478815B2 (en)
EP (1) EP1430242B1 (en)
JP (1) JP4397234B2 (en)
AT (1) ATE296413T1 (en)
DE (2) DE10145914A1 (en)
DK (1) DK1430242T3 (en)
ES (1) ES2242063T3 (en)
TW (1) TW554146B (en)
WO (1) WO2003027545A1 (en)

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Also Published As

Publication number Publication date
JP4397234B2 (en) 2010-01-13
DE10145914A1 (en) 2003-05-08
DE50203218D1 (en) 2005-06-30
ATE296413T1 (en) 2005-06-15
US7478815B2 (en) 2009-01-20
ES2242063T3 (en) 2005-11-01
JP2005504237A (en) 2005-02-10
EP1430242B1 (en) 2005-05-25
DK1430242T3 (en) 2005-09-19
US20040251636A1 (en) 2004-12-16
WO2003027545A1 (en) 2003-04-03
TW554146B (en) 2003-09-21

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